JP2003527496A - Device for controlling the thread lever of a braiding machine and braiding machine - Google Patents

Abstract

(57) [Summary] The present invention relates to a braiding machine (1), which is provided with a device for controlling a thread lever (10), the device comprising an annularly closed cam track (30). ) And a slide (31) belonging to the cam track, provided with a reversing transmission (20), by means of which the rotation direction of the drive motor is reversed, whereby It is of the type in which the upper supply bobbin group is rotated in the opposite direction to the lower supply bobbin group. In order to realize a relatively high limit rotation speed in such a type of braiding machine (1), the slide (31) and the cam track (30) are aligned with the center axis (50) of the braiding machine (1). A central tube (3) located inside a turning surface (32) described by a thread lever (10) rotating about a center and / or wherein the reversing transmission (20) has a large pitch circle diameter; An internal gear fixedly mounted on the internal gear, a pinion rotating in the internal gear, and an external gear rotatably supported on a central pipe having a small pitch circle diameter. Is rotatably mounted on a rotational axis which is fixedly connected to the casing, and the internal gear and the external gear are positively connected.

Description

Detailed Description of the Invention

The invention relates to a device for controlling the thread lever of a braiding machine according to the preamble of claim 1 and a braiding machine of the type described in the preamble of claim 12.

Braiding machines of this type are, for example, Katalog Srirka.
) "Spirka Schnellflechter". According to the catalog, the high-speed braiding machine is capable of a rotational speed of up to about 150 rpm, depending on the number of bobbin groups rotating in the opposite direction each time.

The number of transmission couplings and kinematic parameters required makes it difficult to increase the rotational speed arbitrarily.

An important characteristic value of the braiding machine is the critical speed. This limiting speed depends on several factors. That is, it depends on the type of control of the thread lever and / or on the type of drive connection between the drive member, the reversing transmission and the bobbin support.

The thread lever must, on the one hand, be pivotably mounted above the weft bobbin,
On the other hand, it must be mounted below the warp bobbin.

In this case, the upper end of the thread lever must run above the warp bobbin so that the weft thread to which it belongs is taken up by the thread guide plate in each case. The thread guide plate fixes the movement surface of the weft thread above the warp thread.

The control of the thread lever is usually carried out by a combination of a circularly closed cam track and the associated slide. The cam track is located outside the plane of rotation on which the thread lever rotates during rotation of the weft bobbin.

[0008]   Therefore, the cam track surrounds the entire braiding machine.

However, since the thread lever has a relatively large length, a relatively high moment of inertia is expected. The moment of inertia must be provided as a force by a sliding track pair consisting of a slider and a cam track in order to cause the thread lever to make a quick swiveling motion. Furthermore, the relatively large distance of the cam track from the center of rotation causes a relatively high relative speed between the slider and the cam track, so that a relatively high surface pressure is expected in this case.

On the other hand, the inversion transmission in a braiding machine with a central tube is the main means for causing the upper bobbin support to carry out a rotational movement about the central tube, which is opposite to the lower bobbin support. It has components.

Since such a mechanical transmission has a significant proportion of the required power of the braiding machine, it must always be sought to have a low power consumption of the transmission.

However, in addition to reversing the rotational direction between the lower thread bobbin and the upper thread bobbin, there is also the problem that a predetermined conversion defined by the braiding process must be performed.

The object of the invention is therefore to improve the braiding machine in such a way that a high rpm is obtained.

This problem is solved by the invention having the features of claim 1 and by the invention having the features of claim 12.

According to this, the limit rotational speed of the braiding machine of this type can be increased.
There are two different means.

These means can be realized in one braiding machine independently of one another and in combination with one another.

[0017]   First, the means of claim 1 will be described below.

This partial invention has the advantage that the weft bobbin and the warp bobbin can be favorably accessed in a compact construction of the braiding machine.

Such an advantage is obtained by removing the conventional enclosure of the braiding machine with a stationary cam track and replacing it with a cam track transferred inwards.
This facilitates access to the weft bobbin and the warp bobbin.

In such a partial invention, it is important that the slider and the cam track are located inside the rotation surface defined by the thread lever when the thread lever rotates about the central tube of the braiding machine. is there.

On such a plane of rotation, the thread lever additionally carries out a pivoting movement, whereby the warp thread and the weft thread are woven.

This partial invention reduces, on the one hand, the relative speed between the slider and the cam track. This is because the working circle between the slider and the cam track has a smaller radius than if the cam track is located outside the circle of rotation.

Furthermore, the law of motion of the thread lever is defined by the curvature of the so-called thread guide plate, which forces an exact geometrical shape of the cam track. As a result, the weft yarn is reciprocally swung while always contacting the yarn guide plate.

As the working circle between the cam track and the slider is moved towards the central axis of the braiding machine, the relative speed decreases, in which case the given law of motion of the thread lever is not inconvenient.
To that extent, the working circle between the slider and the cam track is sought to lie inside the circle described by the inner end of the pivot axis. This additionally allows the pivot of the thread lever to be supported in a bore provided in the transmission casing, where the slider and the cam track can be located in the oil bath.

The oil continuation lubrication possible in this way allows a relative velocity between the slider and the cam track, which was heretofore unavailable.

The cam track is arranged on an annular console for simplicity of construction. The annular console is non-rotatably connected to the central tube as a separate component.

Furthermore, the swivel axis is inclined at the end facing the central tube so that it is inclined with respect to the braiding point. The braid point is actually the end of the material to be braided out of the central tube. As a result, an effective turning motion above the warp bobbin and below the weft bobbin is performed with a small force. The reference limiting angle is 45 °, measured in the plane perpendicular to the central axis. Accordingly, the allowable angle range is 45 °>α> 0 °.

If the cam track is additionally inclined by the same angle L as the swivel axis, good surface friction between the slider and the cam track is obtained.

Furthermore, in order to compensate for the tension fluctuations that occur when the thread lever rotates, a thread storage roller is additionally provided, which functions for temporary storage of the weft thread during rotation and which functions as a weft thread. Keep the tension practically constant.

The other dependent claims provide advantageous further configurations of the invention. According to the second partial invention, the casing for housing the transmission of the braiding machine can be made extremely small and compact, which also ensures good accessibility for the weft bobbin and the warp bobbin. ing.

Due to the compact construction of the casing, the resonance characteristics of the braiding machine are also improved, and the rotational speed limit is therefore increased. In principle, this partial invention is based on the reversal effect caused by the pinion rotating in the internal gear. The internal gear ensures that the internally rotating pinion is supported on the driven side of the transmission at the point of action on the external gear with a small pitch diameter. As a result, the rotation direction is reversed.

At the same time, such a planetary gear set makes it possible to adjust the rotational speed characteristic according to the invention, which is necessary for the braiding process.

Special advantages of this sub-invention are also set out in the claims independent of claim 1.

[0034]   This partial invention can also be used in combination with the features of claim 1.

[0035]   Embodiments of the present invention will now be described in detail with reference to the drawings.

[0036]   Unless otherwise specified, the following description applies to all drawings.

[0037]   A braiding machine 1 is schematically shown in the drawings.

[0038]   A central tube 3 is fixedly attached to the machine frame 2.

The central pipe 3 serves in the lower region for receiving the transmission casing 5, which is rotatably arranged on the central pipe 3 on the transmission casing bearing 6.

The drive device 4 causes the transmission casing 5 to rotate. This rotary movement also takes place in the sliding track support 7 which is connected to the transmission casing 5.

A lower bobbin support 8 is arranged in the lower region of the transmission casing 5. Each bobbin support 8 supports one weft bobbin 9.

The weft thread is guided through an opening (not shown) of the thread lever 10 and from there to a diverting device 13 located at the upper end of the thread lever 10.

The thread lever 10 can be swung around a swivel shaft 11. The swivel shaft 11 is movable by a swivel shaft bearing 12.

From the turning device 13, the weft yarn reaches the braiding point 14. The braiding point 14 is arranged on the outer peripheral surface of the vertical member 15 whose peripheral surface is to be braided.

When the longitudinal member 15 is simply conveyed in the vertical upward direction, the weft bobbin makes a rotational movement about the central tube 3 in a predetermined rotational direction. This rotational movement is performed by the drive device 4.

It can be seen that the spring lever 10 defines a plane of rotation which is concentric with the central axis 50 when it rotates about the central axis 50. At the same time, spring lever 10
Makes a swivel motion about the swivel axis 11. The swivel axis 11 is a lower supply bobbin,
That is, it is located above the weft bobbin 9 and is connected to the transmission casing 5 so that the rotational movements of the thread lever 10 and the transmission casing 5 are synchronized.

As a result, the thread lever 10 and the transmission casing 5 rotate about the central tube 3 of the braiding machine in the first rotation direction.

At the same time, when the spring lever 10 rotates about the central axis 50, the slider 31 and the cam track 30 belonging to this slider engage in a form-fitting manner. It is forcibly controlled so that the repetitive vibration motion 35 is performed on the rotating surface 32 defined by 1. This turning motion 35 is performed around the turning shaft 11. This pivoting movement is produced by the course of the cam track 30. The cam track 30 has this course on a closed path about the central axis 50.

The form-fitting engagement between the slide 31 and the cam track 30 thus causes a movement by means of a corresponding moment of the pivot, which movement depends directly or indirectly on the spring lever. It is transmitted to 10. In order to form a braided product with such a device, it is necessary to rotate the warp bobbin 9 in a second rotational direction 29b, which is opposite to the first rotational direction 29a.

For this purpose, a reversing transmission 20 is provided, which reversing transmission 20 comprises
It comprises a conversion stage 23 and an intermediate gear 21.

The reversing transmission 20 changes the rotational movement of the transmission casing 5 to a rotational direction opposite to the first rotational direction and causes the warp yarn carriers 18 each having one warp yarn bobbin 19 to perform it. work. That is, the warp support 18 moves about a central axis 50 in a rotational direction 29b opposite to the first rotational direction 29a, in which case it is guided by the sliding track support 7. Like the warp support 18, the sliding track support 7 is also only partially provided.

As a result, in the region of the sliding track support 7 having the warp thread support 18, the sliding track support 7 and the warp thread support 18 rotate in opposite directions about the central axis 50, and alternately. Runs in and out.

For this purpose, the reversing gearbox 2 with the intermediate gear 21 as the main component
0 works.

The intermediate gear 21 is firmly connected to the sliding track support 7 via an intermediate gear shaft 22. This intermediate gear 21 is a bevel gear, and on the other hand, is attached to the warp support 18.
On the other hand, it is in form-fitting engagement with the inner ring 16. The inner ring 16 is likewise rotatably mounted on the central tube 3 independently of the transmission casing. The inner ring bearing 17 allows the inner ring 16 to rotate about the central tube 3 independently of the transmission casing 5.

Since the transmission casing 5 and the inner ring 16 must have different rotational speeds, a conversion stage 23 is provided as shown in FIGS. The conversion stage 23 is supported by an annular console 24.

[0056]   The annular console 24 is non-rotatably connected to the central tube 3.

[0057]   Based on FIGS. 4 and 5, the conversion stage 23 will be described again in a different embodiment.

In this case, the conversion stage 23 consists of an internal gear 25 rigidly connected to a stationary annular console 24.

[0059]   The internal gear 25 has the largest pitch circle diameter inside the conversion stage 23.

The pinion 26 rolls in the internal gear 25. The pinion 26 is rotatably supported about a rotation shaft 28.

[0061]   The rotary shaft 28 is rigidly connected to the transmission casing 5.

The rotating pinion 26 is engaged with the internal gear 25 on the one hand and
Has an external gear 27 with a small pitch circle diameter. A pinion 26, which also rotates, meshes with the external gear 27.

Therefore, the pinion 26 is constantly engaged with the internal gear 25 having a large pitch circle diameter and the external gear 27 having a small pitch circle diameter, and is centered on the central axis 50 together with the transmission casing 5. , Rotate on the rotation axis 28. This is because the pinion 26 is so forced by engaging the stationary internal gear 25 with its dentition.

Therefore, the rotational movement of the inner ring 16 and the rotational movement of the transmission casing 5 are oriented in the same direction. However, since the direction of rotation is reversed by the intermediate gear 21, the warp support 18 is converted into a rotational movement opposite that of the sliding track support 7.

This is illustrated (absolutely) by the symbols of the first direction of rotation 29a and the second direction of rotation 29b, independently of the respective rotation speed.

During such a movement in the first direction of rotation 29a, the slider 31 moves the stationary cam track 3
0, so in a corresponding device the thread lever is pivoted, as shown, for example, in FIGS.

The turning movement 35 is carried out between the lower turning position 33a and the upper turning position 33b, during which the thread lever 10 is guided around the central axis 50.

As additionally shown for this in FIG. 3, the slide 31 is mounted on a guide lever 44 which is spaced from the geometrical pivot axis 45 of the pivot 11.

Since the swivel shaft 11 itself is rotatably supported, by forming the cam track 30 accordingly, the thread lever 10 is reciprocally swiveled while being guided around the central axis 50. Can be made.

In the embodiment of FIGS. 1 to 4, the swivel shaft 11 is supported on the transmission casing 5.

[0071]   This also applies in principle to the pivot bearing in the embodiment of FIG.

However, in the case of FIG. 5, the swivel axis 11 does not face the direction toward the central tube 3 and is separated from the central tube 3.

Correspondingly, the cam track 30 is provided in an area of the braiding machine which is located outside the surface of rotation 32 and runs on the peripheral surface facing the central tube 3 in the running slide 31. Has an engagement area for.

The cam track 30 is a component part of an annular body surrounding the braiding machine. This cam track can have a relatively small diameter in the embodiment of FIG. 5 by making the reversing transmission as compact as possible.

Therefore, with the compact inversion transmission of the embodiment of FIG. 5, it is possible to raise the limit rotational speed of the braiding machine of this type. Because the slider 31 and the cam track 3
This is because the sliding pair between 0 and 0 is at a relatively low peripheral speed.

The geometry of the transmission casing 5 of FIG. 5 is not to scale. The actual volume of construction of the transmission casing 5 is very small, so that the inner diameter of the annulus with the cam track 30 is correspondingly reduced.

The respective distance-time law of the thread lever movement is defined by the principle contour of the thread guide plate 34.

In the embodiment shown in FIGS. 1 to 4, the slider 31 and the cam track 30 are located inside the rotation surface 32 which the thread lever 10 draws in response to the rotational movement about the central axis 50. There is.

The force introduced into the thread lever for controlling the thread lever originates from the working circle having a smaller radius than the rotation surface 32 drawn by the thread lever 10.

In addition to this, the slider 31 and the cam track 30 are connected to each other by the inner end portion 36 of the pivot shaft 11.
It is located inside. Therefore, in this case, the working circle between the slider 31 and the cam track 30 is located inside the circle described by the inner end 36 of the pivot 11.

Furthermore, FIGS. 1 to 4 show that the swivel shaft 11 is rotatably supported in the hole 37 of the transmission casing 5.

Furthermore, the bearing of the transmission casing is sealed in the central tube and the outer surface of the inner ring 16 and the swivel bearing of the swivel shaft 11 is sealed in the transmission casing by radial sealing members 39a, 39b, 39c. I understand that Therefore, the oil surface 38 inside the transmission casing 5 is formed such that the slider 31 and the cam track 30 are located in the oil bath. The oil-tightly closed transmission casing 5 is optionally provided with suitable drainage screws.

Since the cam track 30 is attached to the annular console 24, there is no wear between the slider 31 and the cam track 30 and there is continuous clean lubrication to the environment, which is extremely This is linked to the advantage of high relative speed and thus extremely high rpm of the braiding machine.

In any case, however, the cam track support, which is the outer circumference of the annular console 24 in the illustrated embodiment, is actually the annular rotation surface 40 defined by the pivot 11.
It is satisfied that it is located on an extension of the central axis 50 of the.

This results in a direct and effective transmission of the cam track 30 to the thread lever 10. This is because the force transmission type slider between the slider 31 and the pivot 11 is short and compact.

In addition to this, additionally, the swivel axis 11 may be tilted in the direction of the braid point 14 at the end 41 facing the central tube 3. Such measures are taken for effective braid geometry and are known from the prior art.

In order to effectively engage between the slider 31 and the cam track 30, the cam track contacts the wall of the cam track 30 at the same angle so that the slider 31 contacts as large an area as possible. It is desirable to incline to do so.

Furthermore, additionally, a yarn accumulating roller 43 is connected to the swivel shaft 11 of the yarn lever 10, and this yarn accumulating roller has a weft groove 46 concentric with the swivel shaft 11. .

By such a means, the change in tension in the weft thread caused by the turning movement of the thread lever 10 between the lower turning position 33a and the upper turning position 33b is compensated.

The geometrically favorable course of the cam track 30, and thus the alternative movement during rotation of the slider 31, is in principle defined by a curved thread triangle. This thread triangle is defined between the braiding point 14 and the deflection device 13 of the thread lever 10 and is located above the envelope end drawn by the warp threads between the warp bobbin 19 and the individual braid points 14. There is.

However, since such a law of motion is well known, the catalog “Spirka-Schnellflechter” is used.
Please refer to. No further mention will be made.

In addition to the embodiments of FIGS. 4 and 5, an internal gear 25 and a rotating pinion 26 are additionally provided.
And the external gear 27 lie in one and the same radial plane 48 with respect to the central tube 3 and are in mesh with each other in this radial plane.

Such a means rotates with the transmission casing 5 and thereby avoids possibly bending moments on the bearing of the pinion shaft, referred to as the rotary shaft 28.

Furthermore, the same outer tooth row of the rotating pinion 26 provides the entire transmission connection, including the conversion between the drive motor and the inner ring 16.

This means that the pinion 26 directly meshes with the internal gear 25 and the external gear 27, and in this case, the intermediate gear 21 is loaded by the driven side of the external gear 27,
At the same time, it engages a dentition ring mounted on the upper bobbin support 18.

For this purpose, the intermediate gear is fixedly connected to the transmission casing 5 and comprises an internal gear 25,
Radial plane 4 in which rotating pinion 26 and external gear 27 mesh with each other
It is mounted on the intermediate gear shaft 22 located above the gearbox 8.

[Brief description of drawings]

[Figure 1]   It is a figure which shows the 1st Example of this invention.

[Fig. 2]   FIG. 5 shows an embodiment of the invention with a tilted pivot.

[Figure 3]   FIG. 7 is a schematic view of an inner cam track with engaged slides.

[Figure 4]   FIG. 3 shows an embodiment of the invention with an advantageous configuration of the reverse gear.

5 is a diagram showing the reversing device of FIG. 4 in a braiding machine having a slider located outside the plane of rotation.

[Explanation of symbols]

1 braiding machine, 2 machine frame, 3 central pipe, 4 drive device, 5 transmission casing, 6 transmission casing support, 7 sliding track support,
8 lower bobbin support, 9 weft bobbin, 10 thread lever, 11 swivel axis, 12 swivel axis bearing, 13 turning device, 14 braiding point, 15 vertical member to be braided around, 16 inner ring, 17 inner ring bearing , 18 warp support, 19 warp bobbin, 20 reversing transmission, 21 intermediate gear,
22 intermediate gear shaft, 23 conversion stage, 24 annular console, 25 internal tooth ring, 26 rotating pinion, 27 external gear, 28 rotating shaft, 29a
1st rotation direction, 29b 2nd rotation direction, 30 cam track, 31 slide, 32 rotation surface, 33a lower turning position, 33b upper turning position,
34 thread guide plate, 35 swivel motion, 36 inner end, 37 hole, 38 oil surface, 39a, 39b, 39c radial seal member, 40
Rotating surface, 41 end portion, 42 inclination angle, 43 yarn accumulating roller, 44
Guide lever, 45 turning axis, 46 weft groove, 48 radial plane,
50 central axis

─────────────────────────────────────────────────── ─── [Continued summary] Has been done.

Claims (15)

[Claims] 1. A device for controlling a thread lever (10) of a braiding machine (1), comprising a circular closed cam track (30) and a slider (30) belonging to this cam track (30). 31) in which the thread lever (10) has a swivel axis (11), which swivels (11) above the lower supply bobbin (weft bobbin 9). The transmission casing (5) being connected to the casing (5)
Is driven to rotate about a central tube (3) of the braiding machine (1) in a first direction of rotation (29a), and the thread lever (10) rotates the transmission casing (5). Draw a plane of rotation (32) with, and on this plane of rotation (32), slide (31
) Causes the reciprocating revolving motion (33a, 33b) about the revolving shaft (11), and the rotational motion (29a) of the transmission casing (5) is the intermediate gear (21).
A reverse transmission device (20) provided with a reverse rotation mechanism (29b), which is opposite to the first rotation direction (29a), and is transmitted to the bobbin support of the warp bobbin (19). Controlling the thread lever (10) of the braiding machine (1), characterized in that the slider (31) and the cam track (30) are located inside the surface of revolution (32). Device for doing. 2. The slider (30) and the cam track (30) make a distance with respect to the central axis (50) smaller than the circle described by the inner end (36) of the pivot axis (11). The device of claim 1, wherein the device is located. 3. Device according to claim 2, characterized in that the swivel shaft (11) is mounted in a hole (37) provided in the transmission casing (5). 4. The transmission casing (5) and the hole (37) of the transmission casing (5) are oil-tightly closed (39a, 39b, 39c), and the slider (
Device according to claim 3, characterized in that 31) and the cam track (30) are located in an oil bath. 5. A cam track (30) is provided on an annular console (24), said annular console (24) being non-rotatably connected to the central tube (3). The apparatus according to claim 1. 6. A device according to claim 5, wherein the annular console (24) is located inside the transmission casing (5). 7. The cam track support (eg, annular console 24) is actually
7. Device according to claim 6, which is arranged on an extension of the plane of rotation (40) defined by the swivel axis (11) to the central axis (50). 8. The method according to claim 1, wherein the end (41) of the swivel axis (11) facing the central tube is inclined with respect to the braid point (14). apparatus. 9. The inclination angle (42) of the central tube (3) with respect to the radial direction is 45.
9. The device according to claim 8, which is less than °. 10. The cam track (30) has the same tilt angle (4) as the pivot axis (11).
2) The device according to claim 8 or 9, which is tilted. 11. A thread accumulating roller (4) is attached to a pivot shaft (11) of a thread lever (10).
3) are connected and are preferably concentric with the swivel axis (11).
Device according to any one of claims 1 to 10, wherein 6) is provided. 12. A braiding machine (1) comprising a central tube (3) and the central tube (3).
And a casing (5) which is driven to rotate in a first rotation direction (29a) about the center of the casing (5), the casing (5) being provided with a bobbin support (8) for the lower supply bobbin (9). ) Is mounted and an upper bobbin support (18) for the upper feed bobbin (19) is provided, the upper feed bobbin (19) also rotating about the central tube (3). Between the lower feed bobbin and the upper feed bobbin, a form-locking reversing gearbox (20) is provided with an intermediate gear (21) which is rotatably supported and which has an intermediate gear (21). On the inlet side, the casing rotation direction (
29a), on the outlet side, a second direction of rotation (29b) opposite the first direction of rotation (29a) is produced, in this second direction of rotation the upper supply bobbin (19). ) Above which the bobbin support (18) is loaded, in particular of the type having the preamble of claim 1 or the device according to any one of the preceding claims: Device (20) with large pitch circle diameter, central tube (3)
An internal gear (25) fixed to the internal gear (25) and a pinion (26) rotating in the internal gear (25).
) And an external gear (27) rotatably supported on the central tube (3) with a small pitch circle diameter, and (b) a rotating pinion (26) has a casing (5). A braiding machine, which is rotatably supported by a rotating shaft (28) that is immovably coupled to, and (c) an internal gear (25) and an external gear (27) are shape-connected. 13. The internal gear (25), the rotating pinion (26) and the external gear (27) mesh with each other in the same radial plane (48) of the central tube (3). The described braiding machine. 14. A rotating pinion (26) comprises an internal gear (25) and an external gear (25).
27) directly meshing with the intermediate gear (21) being supported by a shaft (28) which is loaded by the driven side of the external gear (27) and is rigidly connected to the casing (5), Braiding machine according to claim 12 or 13, wherein at the same time the upper bobbin support (18) engages the toothed ring on which it is mounted. 15. The braiding machine according to claim 12, wherein the rotational speed ratio of the rotational speed of the external gear (27) to the casing (5) is 3: 1.